Two-fluid signaling lubricating system



Nov. 20, 1962 e. H. AC KER TWO-FLUID SIGNALING LUBRICATING SYSTEM 5Sheets-Sheet l Filed Nov. 16. 1960 'GEORGE H. ACKER ATTORNEYS Nov. 20,1962 e. H. ACKER 3,064,759

TWO-FLUID SIGNALING LUBRICATING SYSTEM Filed NOV. 16. 1960 5Sheets-Sheet 2 ii A FIG 6 FIG l9 NVENTOR GEORGE H. ACKER TTORNEYS Nov.20, 1962 G. H. ACKER TWO-FLUID SIGNALING LUBRICATING SYSTEM 5Sheets-Sheet 3 Filed NOV. 16, 1960 Q i m INVENTOR.

GEORGE H. ACKER ATTORNEYS v Nov. 20,1962 G. H. ACKER 3,064,759

TWO-FLUID SIGNALING LUBRICATING SYSTEM Filed Nov. 16, 1960 5 Sheets$het4 TO BEARNG A TO BEARING B FIG l6 TO BEARINGA T0 BEARING B FIG I?INVENTOR.

' GEORGE H. ACKER 1 "I y w"?! ATTORNEYS Nov. 20, 1962 G. H. ACKERTWO-FLUID SIGNALING LUBRICATING SYSTEM 5 Sheets-Sheet 5 Filed Nov. 16,1960 32 o If FIG 20 INVENTOR.

GEORGE H. ACKER ATTORNEYS United States Patent Ofiice 3,064,759 PatentedNov. 20, 1962 7 TWO-FLUID SIGN LIIIG LUBRICATING SYSTEM This inventionrelates generally, as indicated, to a twofluid signaling lubricatingsystem and more particularly to a lubricating valve and system providinghigh lubricating pressures for lubricants automatically to lubricateextensive mill equipment.

In past practice, lubricants such as grease have been purchased in 4001b. drums, and the lubricant reservoirs of the individual lubricatingsystems in a particular mill or plant filled from such drums. Somecompanies have found it possible to reduce their lubricating costs bybuying the lubricant in bulk lots of 10,000 to 20,000 lbs., delivereddirectly from the lubricant manufactory in tanks holding such amounts,and transferred by suitable pumps from such truck-transported tanks tosimilar tanks located within the mill. There is economy in the bulkpurchase of the lubricant itself; the cost of moving the 400 lb. drumsaround the mill is eliminated, loss through residual grease left in the400 lb. drums is eliminated, and hazard of lubricant contamination isminimized. From such a bulk central storage tank, the lubricant ispumped through a header passing near all of the lubricating systemcontrol units serving the particular mill and valved branch lines fromthis header permit renewing the lubricant supply in the individuallubricant system reservoirs without exposure to external contamination.

In accordance with the present invention this lubricant distributionheader is placed under a constant high pressure and the multiplicity oflubricating systems in such mill are operated from this high pressureheader directly. This eliminates the requirement for grease storagereservoirs and pumps normally employed to operate each of the individuallubricating systems.

It is then a principal object of the present invention to provide alubricating system facilitating bulk purchase of the lubricant at aprice advantage and considerably reducing the in-plant handling costs ofsuch lubricant.

For a variety of reasons, line breakage in a line leading to anyparticular bearing to be lubricated or blockage of such line mayoccasionally occur. Accordingly, a system providing a signal indicatingthe occurrence of and location of such breakage or blockage as closelyas possible is to be highly desired. Furthermore, a system which willby-pass any such breakage or blockage so that all of the other bearingsserved by the lubricating system will be lubricated in the normal manneris also obviously desirable.

In such lubricating system, metering of requisite amounts of lubricantto the bearings is customarily accomplished by displacement resultingfrom movement of pistons in cylinders under differential pressures. Highpressures are usually necessary to accomplish this, and highdifferential pressures present a hazard of by-passing lubricant aroundthe displacement pistons, destroying the accuracy of metering. It istherefore advisable to provide relatively equal at-rest residualpressures in such a system.

It is accordingly a further important object of the present invention toprovide such a lubricating system capable of metering lubricant to thebearings under high pressures and yet closely balanced at-rest residualpressures.

7 It is yet another important object to provide a lubricating systemhaving a localized signal of line breakage or blockage.

A further important object is the provision of a lubricating systemwherein the lubricant will by-pass all but the valve having the blockedor broken line.

Another object is to provide a two-fluid lubricating system which willhave low residual substantially identical at-rest pressures for eachfluid, substantially eliminating valve leakage past piston lands.

It is yet another object to provide a lubricating system which may bevery extensive and yet which can be programmed to operate automatically.

Other objects and advantages of the present invention will becomeapparent as the following description proceeds.

To the accomplishment of the foregoing and related ends, the invention,then, comprises the features hereinafter fully described andparticularly pointed out in the claims, the following description andthe annexed drawings setting forth in detail certain illustrativeembodiments of the invention, these being indicative, however, of but afew of the various Ways in which the principles of the invention may beemployed.

In said annexed drawings:

FIG. 1 is a diagrammatic fragmentary layout of a lubricating system inaccordance with the present invention;

FIG. 2 is a top plan view of a manifold lubricating valve which maypreferably be employed with the present invention;

FIG. 3 is a front elevation of such manifold valve as viewed from thebottom of FIG. 2;

FIG. 4 is an end elevation of such manifold valve as seen from the leftof FIG. 2;

FIG. 5 is a vertical section of the inlet end block of such valve takensubstantially on the line 5-5 of FIG. 2;

FIG. 6 is a vertical section of such inlet end block taken on the line66 of FIG. 5;

FIG. 7 is a vertical section of the outlet end block of such valve takensubstantially on the line 77 of FIG. 2;

FIG. 8 is a vertical section of such outlet end block takensubstantially on the line 8-8 of FIG. 7;

FIG. 9 is a vertical section taken on the line 9-9 of FIG. 2 of one ofthe valves in such manifold;

FIG. 10 is a horizontal section of such valve taken on the line 1010 ofFIG. 9;

FIG. 11 is a horizontal section of such valve taken on the line 1111 ofFIG. 9;

FIG. 12 is a vertical fragmentary section of such valve taken on theline 1212 of FIG. 10;

FIG. 13 is a vertical section of such valve taken on the line 1313 ofFIG. 10;

FIG. 14 is a vertical section of such valve taken on the line 1414 ofFIG. 9;

FIG. 15 is a vertical section of such valve taken on the line 15-15 ofFIG. 9;

FIG. 16 is an enlarged section identical to that of FIG. 9 illustratingmore clearly the details of such valve;

FIG. 17 is a sectional view similar to FIG. 16 illustrating such valvein its alternate position;

FIG. 18 is a fragmentary section taken substantially on the line 13-18of FIG. 2 illustrating the details of the low pressure cut-off valvemounted on the bearing outlets of each of the valves in such manifold;

FIG. 19 is a fragmentary diagrammatic view of an alternative form oflubricating system in accordance with the present invention; and

FIG. 20 is a wiring diagram of the rudiments of an electrical systemthat may be employed to operate a lubricating system in accordance withthe present invention.

The System-FIGURE I Referring now to the annexed drawing and more particularly to FIG. 1, the lubricating systeiri illustratedfis designedfor time-clock programmed operation, and for employment where lubricantis continuously supplied un= der high pressure, e.g., 2,000 psi, fromsome central source or alternatively as hereinafter described fromconveniently positioned pumps and reservoirs such as those commonlyemployed in present lubrication practice.

In FIG. 1, a lubricant supply line 1 is teed oil as shown at 2 from thepressure header 3. The pressure header 3 containing the required greaseor oil may extend throughout the mill from the aforementioned centralsupply and a pump as shown or several pumps may be employed to raise andmaintain a pressure therein of, for example, 2,000 psi. Such lubricantsupply line 1 is provided with a shut-off valve 4 and continues throughto the first valve manifold 5 and then as shown at 6 to a further valvemanifold 7 and to other and further valve manifolds as indie'ated at 8.Whereas only three have been illustrated in FIG; 1, it will readily beunderstood that as many valve manifolds may be employed in such systemas required to lubricate the particular mill or equipment. Suchlubricant supply line is plugged as shown at 9 at the end of the lastvalve manifold 8 in such system. The shut-off valve 4 may be controlledby a solenoid of conventional type or preferably, as illustrated, by anair motor 10, such motor being supplied with air pressure through line ll, such'air pressure being controlled by solenoid operated air valve 12.Air for operation of the motor 10 may be provided by header 13 or fromany convenient source of air under pressure. In operation of the system,the air motor operated shut-off valve 4 will normally be closed.

Also provided is a fluid reservoir 15 for a fluid such as ordinaryhydraulic fluid. An air operated pump 16 as, for example, a conventionalbell type pump may be provided to pump the fluid from the reservoir 15at high pressure to a fluid supply line 17 through which all of thevalve manifolds 5, 7, 8 etc. are connected in series as in the case ofthe lubricant supply line .1. A normally closed solenoid valve 18 isprovided in air supply line 13 controlling the operation of pump 16.Whereas an air operated pump is illustrated, it will readily beappreciated that an electric motor driven pump may equally well beemployed and, if such is the case, a conventional motor starter wouldthen be employed in place of valve 18.

Ahead of the first valve manifold 5 an accumulator 20 is providedinterconnecting the lubricant supply line 1 and the fluid supply line17. This accumulator consists of a closed end cylinder in which aclosely fitting axially free-sliding piston 21 is inserted. One end ofthe accumulator cylinder is teed into the lubricant supply line 1 andthe other end of the accumulator is teed into the fluid supply line 17.

A fluid return line 23 is provided between the fluid supply line 17 andthe fluid reservoir 15. A shut-off valve 24, normally open, may becontrolled by air motor 25. The air motor 25 is connected to air line 26which is controlled from the solenoid operated air valve 18 controllingthe fluid pump 16. However, a solenoid operated valve may'optionally beprovided energized by the same electric circuit as that shown. Betweenthe shut-off valve 24 in the return line 23 and the fluid reservoir 15 apressurelimiting check valve 27 opening, for example, at 700 psi. isprovided,.having the effect of limiting the relief of the pressure inthe fluid supply line to that pressure level.

When a time clock 30 or other .programming'means makes an energizingelectrical contact within controlcenter 31, the lubricant shut-off valve4 is opened through solenoid valve 12 and also the fluid pump motor 16is started, while the fluid relief shut-off valve 24 is closed. Theaccumulator 20 will be partially filled with lubricant atths point andit may receive additional lubricant from the inflow resulting when theshut-off valve 4 is opened.

4 The fluid pump 16 will build fluid pressure higher than the 2,000 psi.lubricant pressure, and will force the lubricant from the accumulator 20back into the supply line 1. When the lubricant has been displaced andthe accumulator piston 21 cannot move further, the fluid pressure willrise as required until it reaches a magnitude of approximately 3,000psi. at the valve manifolds. Ahigh pressure switch 32 installed in thefluid outlet of the last manifold 8 at the distal end of the system willmake an electric contact to energize a reset relay 33 when such 3,000psi. pressure is obtained at that point. This will normally indicatecompletion of the lubricating cycle causing the shutoff valve 4 toclose, the fluid pump 16 to stop, and the relief cut-off valve 24 toopen.

At this point, the pressure differential between the fluid supply line'17 and the lubricant supply line 1 will have forced the pilot pistonsof the valves as hereinafteride scribed toward the lubricant end oftheir cylinders and the metering pistons of these valves will have beenforced toward the fluid end displacing lubricant to half of the bearingsserved by the system. With the fluid pump 16 stopped, the pressurethroughout the fluid supply 17 will rather quickly. reduce toapproximately 7-00 psi. The pilot pistons of the valves will also serveas very small accumulators, and as the fluid pressure in the systemfails,

the entrapped air in the lubricant supply system beyond the cut-offvalve 4 will tend to sustain the lubricant pressure temporarily, and asthe fluid pressure falls the pilot pistons will be forced into theirnormal positions, causing displacement of lubricant to the other half ofthe interconnected bearings. Fluid willalso be displaced from theaccumulator 20 as the fluid pressure drops, until fluid and lubricantpressures are equalized at that point. Completion of valve operationduring this relieving cycle is insured by the relative size or flowresistance of the conduit between the accumulator and the lubricantsupply line 1 to govern the rate of relief of lubricant pressure, oralternatively, closing of the cut-off valved may be delayed beyondstoppage of the pump 16 and opening. of valve 24.

While the system illustrated employs only a single accumulator, it willbejunderstood that a plurality of ac cumulators can be so located in anextensive lubricating system to offset the effect of high lubricant flowresistance hindering equalization of fluid and lubricant pressures inthe system at rest. Discharge line check valves at the hearing pointsserve to maintain a 700 p.s.i. pressure in such discharge lines and thusequalize fluid and lubricant pressure, which is to be desired tominimize by-pass of fluid or-lubricant around the lands of the valvepistons.

When the fluid pressure at the remote or distal end of the fluid supplyline 17 falls to a value slightly greater contact that will clear theelectrical controls so that a new cycle of operation can be initiated inthe system.

Without such contact being made, a new cycle cannot be started and theprogramming timer will then preferably make a warning indication.

A high-low pressure switch 35 is provided in the fluid supply line 17ahead of the first valve manifold 5. This switch is set to make acontact at, for example, 3,500 psi. so that if a valve malfunctions andcauses any of the high pressure by-pass valves in the manifold to openas hereinafter described, such switch will produce a high pressurecontact energizing an alarm signal. This alarm signal may take the formof a signal light36 in a bank 37 of suc'n signal lights. Similarswitches 38 and 39 in the fluid supply line 17 may be provided for therespective manifolds 7 and 8, such switches energizing signal lamps 42'and 41 respectively upon the attainment of the.

such devices are provided between all manifolds, the'mal- 1 functioningone may be identified as that beyond which no high pressure indicationis given.

It will be obvious that conventional limit switches can be installed inplace of such high-low pressure switches to be operated by physicaldisplacement of the manifold bypass valve members as hereinafterdescribed to serve this same end. The making of the low pressure contacton the pressure switch located ahead of the first manifold may be set ata pressure below the 700 p.s.i. relief pressure as, for example, 650p.s.i., and utilized directly to energize an alarm signalling a leak ineither the fluid or lubricant supply lines since these pressures areequalized in the static condition through the accumulator.

Similar low pressure contacts on the high-low pressure switches 35, 38and 39 in the fluid supply line may be employed to indicate remotely themalfunctioning manifold, since those manifolds on the pump side of themalfunctioning line will relieve quickly in those instances where thefluid relief is accomplished entirely through the fluid supply line, andrelief beyond .the malfunctioning manifold will be delayed by thenecessity of relieving through the restricted by-pass in the enteringend block of the defective manifold. When the lubricating system isextensive, and operating cycles are relatively frequent, it is possibleto increase the rate of relief by running a relief line 43 from theleaving end block of the last manifold back to the reservoir 15 through,for example, a 3,000 p.s.i. check valve 44. A by-pass in such optionalline 43 must be provided between this 3,000 psi. pressure control valve44 and the 700 p.s.i. valve 27. This by-pass line 45 may then beprovided with a shut-off valve 46 actuated by an air motor 47 connectedto air line 26 and operated in unison with the regular relief shut-offvalve 24.

Particularly where such dual-end relief is provided, the low pressurecontacts of high-low pressure switches 35, 38 and 39 in the fluid supplyline between manifolds must all be required to make low pressure contactbefore the system may be recycled.

Instead of employing separate contacts on the high-low pressure switches35, 38 and 39, a further low pressure switch 48 may be employed in fluidline 17 energizing warning light 49 when the pressure falls to 650p.s.i. to indicate a broken main line. This switch may preferably beplaced in front of the first manifold 5 as shown.

It will, of course, be realized that the indicated fluid pressures areexemplary only and that other fluid pressures could be employed. Theonly thing important is the difference in fluid pressures obtainedbetween the fluid and lubricant supply lines.

The Valve Manifold An illustrative valve manifold is shown in FIGS. 2, 3and 4 and the details of an individual valve are shown in FIGS. 5through 18 inclusive. The valve manifold includes: an inlet end block 50having a mounting plate 51 thereon; valves 5'2, 53, 54 and 55, all ofwhich are identical in form; and outlet end block 56 also having amounting plate 57 thereon. It is noted that all of the blocks 50, 52,53, 54, 55 and 56 are of the same rectangular shape and four alignedholes are provided in each for four tie bolts 58, 59, 60 and 61 whichpass through the end blocks and all intermediate valves to hold them ina compact assembly. Such tie bolts will be secured by nuts and washersas shown at the outlet end block 56 and gaskets 62 will be employedseparating all of the segments of such an assembled manifold. The fourtie bolts, of course, will pierce the gaskets 62, and three additionalholes will be required to form continuations of the high pressureby-pass passages, the lubricant passage 1, and the fluid passage 17through the manifold valves from one end block to the other. It is notedthat since only those circular openings permitting passage from theports of one valve block directly to those of the adjacent block arerequired in the gaskets, very little of the adjoining valve blocksurfaces are exposed to high hydraulic pressures,

and accordingly strains of no great severity will be imposed on the tiebolts when the manifold assembly is subjected to working pressures.

Each of the valves 52 through 55 inclusive is provided with twolubricant outlets as shown on :valve 52 at 64 and 65. Each such outletis provided with a low pressure spring loaded cutoff 6-6 and 67 as arethe outlets of the other valves in such manifold, such low pressurecutoffs being hereinafter described in more detail.

The passages and ports of the valves are drilled from a substantiallyrectangular steel block and where desired passages must be started fromthe outer surfaces of the valve block, but must be closed at suchsurface, it is the practice to accomplish this by laying a somewhatoversized soft steel ball in the external opening and spot welding it inplace. The result is indicated by an internal hemisphere projecting intothe passage.

The inlet end block is shown in more detail in FIGS. 5 and 6 and theoutlet end block is shown in detail in FIGS. 7 and 8. The inlet endblock has a through bore forming an inlet port 70 for the manifold forthe lubricant line '1 and an inlet port 71 for connection of fluid line17, both such ports 70 and 71 being preferably threaded to facilitatethe connection of the supply lines thereto. Whereas the port 70 for thelubricant line leads directly through the block, the porting from thefluid connection 71 leads to the end of high pressure spring loadedby-pass piston 72. The pressure of spring 73' against such piston isbacked up by means of nut 74 and the piston 72 extends through such nutexteriorly of the block as shown at 75. Accordingly, when fluid pressureon the end of the piston 72 exceeds the force of the spring 73 holdingit in position, the piston 72 will move to the left permitting fluid toby-pass through passage 76 leading through the face of the block. Thepassage 76 continues through the manifold in the form of a high pressureToy-pass line and the outlet end block 56 is drilled on its inner faceto receive this high pressure by-pass line or passage as shown at 77 inFIG. 8. In the outlet end block 56, the high pressure by-pass passage 77rejoins the fluid line and such fluid line is provided with a threadedoutlet port 78 for a further extension of the fluid line 17. The fluidin the inlet end block will normally pass outwardly through port 79through the manifold and into the fluid port 80 in the outlet block 56and then outwardly through the fluid outlet port 78. The outlet endblock 56 is also provided with lubricant outlet port 81 for continuationof the lubricant line 1. Each of the inlet and outlet end blocks isprovided with four apertures as shown at 82 for accommodation of thefour tie bolts 58, 59, 60 and 61.

=Fluid will be forced through the high pressure by-pass line 76 only inthe case of a malfunction or blockage in one of the valves 52 through 55in the manifold, and return of the valves, as hereinafter described,beyond the one malfunctioning can be provided by relieving the fluidpressure at the far end of the last manifold. This can be accomplishedby providing a .by-pass passage around the piston 72, such passagehaving a reduced diameter por' tion as shown at 83, with a one-way checkvalve in the form of a ball 84 loaded by spring 85 held-by plug 86,providing a one-way by-pass for fluid flow from the high pressurepassage 76 to the entering fluid port 71.

The Valve The valve as disclosed in FIGS. 9 through 16 is shown in anormal or rest position. The fluid passages in the position shown arefluid filled under, for example, 700 p.s.i., the relieved presure, andthe lubricant passages between operating cycles being substantially atthat pressure.

Referring more particularly to FIGS. 9 and 16, at the start of anoperating cycle, lubricant pressure is raised to 2,000 p.s.i. and fluidpressure to 3,000 p.s.i. Fluid enters inlet passage (FIG. 11) movingthrough passageway 91 and around ,the relieved portion 92 of pilotpiston 93, through passage 94 and then across to passage 95 (FIGS. and13) and through relieved portion 96 of the main or metering piston 97and out port 98 to the next valve.

As shown perhaps more clearly in FIG. 16, the pilot piston 93 and themain piston 97 are horizontally mova ble' in respective cylindricalbores 99 and 100, the bore 99 being closed by plugs 101 and 102 and thebore 100 being closed by plug 103 and adjustable indicator 104.

Both the pilot and main pistons are multi-land pistons and are providedwith appropriate sliding seals where required as shown.

Lubricant enters the valve member through throughbore 105 aligned withthe inlet port 70 and the outlet port 81 in the inlet and outlet endiblocks respectively. Such through-bore 105 is connected by passage 106to the cylindrical bore 99 of the pilot piston 93 adjacent the plug 101as seen more clearly in FIG. 16.

At the stime time that theepbmsuloal ghmMFWYMF At the same time that thefluid is traversing the path above indicated, fluid enters passageway107 (FIG. 11) and acts on the right-hand end 108 of the pilot piston toforce that piston to the left. Lubricant within the bore 99 of the pilotpiston will be displaced by such piston movement back into the bore 105which is a portion of the supply line 1 until the central annular relief109 on the pilot piston 93, which connects with the lubricant supplythrough central longitudinally extending passage 110 in the pilotpiston, uncovers the passage 111 leading to the left hand end of themain piston97.

This opposite position of the pilot piston is shown in FIG; 17.

The annular relieved portion 112 of the pilot piston 93 will then be inposition to connect passage 113 leading from the right hand end of mainpiston 97 through the discharge passage 113 leading to bearing B.According-ly, the lubricant pressure in passage 111 permitted bymovement of the pilot piston will provide a lubricant pressure on theleft-hand end 115 of the main piston 97 forcing such piston to the rightuntil its indicator stem 116 is checked by the adjusting screws in theindicator bonnet 117. The lubricant displaced by movement of the mainpiston to the right is forced into passage 113 and through the relievedportion 112 of the pilot piston 93 outwardly through passage 1-14 tobearing B.

Referring to FIG. 10, it is noted that movement of the main piston 97,and thus the relieved portion 96, closes olf port 95 and uncovers port118 thus interconnecting, through the relieved portion 96, port 98 andpassage 118. Movement of the main piston 97 beyond this point isadjustable, since an adjustable stop is pro vided in the bonnet 117 forindicator stem 116, this adgistment regulating the volume displacementto hearing The movement of the pilot piston 93 to the left cuts off thefluid path from the entering port 90 around the relieved portion 92 ofthe pilot piston, and movement of the main piston to the right cuts offport 95 and thus the connection between port 95 and port 98 to the nextvalve. However, the left hand movement of the pilot piston 93 uncoversport 119 (FIGS. 11 and 17), so that fluid can flow from passageway 107through the chamber 120 past the end of thenow shifted pilot piston 93as shown in MG. 17. Movement of the main piston 97 to the right connectsports 98 and 118, port 118 being connected-to port 119 through passage121 as shown in FIG; 13 and in dotted lines in FIG. 15. This thenenables fluid to take the alternate flow route indicated similarly tooperate the next valve.

If, however, the discharge line leading to bearing B becomes plugged,displacement of the lubricant from the right ofithe main piston isprevented, but the pilot piston 93 nonethelessmoves to the left. As aresult, both the fluid'pa'ssages 94, 95 and 121, 113 are blocked. (Note8 FIG. 13.) The resulting stoppage of the fluid with continued fluidpump operation causes the fluid pressure between the pump and theblocked valve to rise and at, say, 3,500 p.s.i., the high pressureby-pass fluid valve shown in FIG. 5 in the entering end block of themanifold is opened against its retarding spring 73, permitting suchfluid to enter the high pressure by-pass line 76. In the valve, thisby-pass line is in the form of a small diameter M through bore 122aligned with the passage 76 in the ip inlet end block and the passage 77in the outlet end block.

It will readily be seen that outward movement of the stem 75 of the highpressure bypass valve may be employed to actuate a limit switch tocomplete an electric alarm circuit as the pressure switch 35 energizesthe alarm signal 36.

When thehigh pressure by-pass valve in the entering block of themanifold opens, fluid flows through the high pressure by-pass passage tothe leaving end block 7 p where it reenters the fluid line. Since themain piston in that particular valve will still be in the rest position,

or at the left, the fluid will move through port 80 into outlet 98 andflow around the main piston relief from port 98 to port 95. The fluidwill then move through passage 94 across the relieved portion 92 of thepilot piston 2 5' 93 which will still be at the right and pressure willthen build at the right hand end of the pilot piston entering thechamber 120 of such valve through port 107. As the pilot piston 93 isforced to the left, it tends to close off communication between passage94 and the port 107 through relieved portion 92. The length of the landat the extreme right of the pilot piston 93 should be such that beforecommunication between passage 94 and port 107 is completely cut ofl itwill have started to uncover port 119 which will assure completeleftward movement of the pilot piston, causing movement of theassociated main piston to the right. Thus, it can be seen that with thisvalve it is possible to actuate such valve from either end of themanifold and accordingly all valves on either side of the malfunctioningvalve will operate properly.

When the high fluid pressure has permeated the fluid system, and allvalves have operated as described moving the pilot and main pistons tothe positions shown in FIG.

17, the fluid pressure will be reduced or relieved to approximately 700p.s.i. through operation of switch 32 thus lowering the fluid pressure.This makes the lubricant at 2,000 p.s.i. operative on the left hand endsof all the pilot pistons 93 substantially simultaneously. The pilotpiston in the valve nearest the fluid source will move to the right asthe fluid in chamber 120 displaced by such 5 movement is returnedagainst 700 p.s.i. pressure to the reservoir 15.

The righthand movement of the pilot piston 93 will reconnect thelubricant pressure from passage to 113 as shown in FIG. 16 leading tothe righthand end of the main piston 97, thus moving the main piston tothe left and displacing lubricant from chamber 130 through pass-age 111around the relieved portion 131 of the pilot piston 93 and out throughpassage 13 2 through the discharge connection 133 to hearing A,returning the valve 6 from the FIG. 17 to the FIG. 16 rest position. The

next valve in line then returns similarly, the fluid in chamher of suchvalve being relieved by fluid passage through outlet port 98, passageway94, relieved portion 92, and inlet passage 90 of the first valve. Allthe valves 6 in the system are thus progressively returned.

75 position prevents return through the alternate route from 9 port 119through port 118. Consequently, all valves following the malfunctioningone are held in their fluid high-pressure position and the fluidpressure beyond the malfunctioning valve remains high. The high-lowpressure switches 35, 38 and 39 between manifolds in the fluid line canthen be utilized to signal the location of the malfunctioning manifold.

Return of the valves beyond the malfunctioning one can be provided byrelieving the fluid pressure at the far end of the last manifold as perline 43 in FIG. 1. Preferably, the passage including the restrictedportion 83 and the one-way spring loaded check valve 84, 85 will beprovided between the high pressure by-pass 76 and the fluid inlet 71 ineach inlet end block of each manifold as shown in FIG. 5. Suchconstruction then permits completion of operation of all of the valvesby relieving fluid pressure beyond the malfunctioning valve by theone-way bypass relief valve in the inlet end block of the manifold andall of the pilot piston valves in the particular manifold will berelieved through this by-pass passage. Thus, the relieved by-passpassage 76, 122 and 77 will provide the relief of pressure in the lastvalve in the manifold through port 98 and, since the main piston in thatvalve will be to the right as shown in FIG. 17, port 98 will beconnected vw'th passages 118, 121 and 119' to the chamber 120, thusrelieving the same. Valves beyond the malfunctioning manifolds will thenbe operated in the normal manner. The restricted passage 83 (FIG. may besized to slow down the return of fluid by that route, and by such delaya signal of malfunction can be produced by means of the operating systemwith the high-low pressure switches being employed to locate themalfunctioning manifold from a remote point. It will, of course, beunderstood that such remote indication may not be required and in thatcase out-of-phase position of any valve indicator stem 116 will pinpointa malfunctioning valve.

Referring now to FIGS. 2, 3, 4 and more particularly to FIG. 18, a lowpressure cut-off mechanism 66 is provided for each of the bearingdischarge outlets on each of the valves in the manifold. These lowpressure cutoff mechanisms are brazed in place on the valve face,registering in the recess at the bearing discharge opening. Thesecut-ofi valves are each provided with plungers 140, such plungersextending transversely of outlet passages 141 and through spring housing142. The plungers are provided with an annular shoulder 143 engagingspring 144 and a suitable seal 145 may be provided surrounding theplunger. Under normal lubricant pressures, the plunger will be held inthe dotted line position shown at 146 clear of the discharge passage141. When the pressure within such passage 141 drops below a nominalvalue, say 300 p.s.i., the pressure of spring 144 becomes greater thanthe lubricant pressure and the valve piston14t crosses the passage 141and thereby blocks it as shown in the full line position in FIG. 18. Itshould be noted that the protruding low pressure cut-off valve stem 149serves as an indicator of the position of that valve. In starting thesystem, this valve can be blocked open man ally to permit filling thelines and the discharge line pressure will then hold such valve open. Inthe event of discharge line failure, it will close and the position ofthe protruding stem will indicate the affected discharge line.

It is possible but improbable that a hearing may become so plugged withsolids that lubricant penetration under the pressure provided i.e.,2,000 p.s.i., by such lubricating system is not possible. It is moreprobable that a loose connection in or rupture of a discharge line fromthe measuring valve to the hearing may prevent lubricant reaching thebearing. To permit a warning signal to be given in either eventuality,the lubricating system includes check valves 147 and 148 so that 700p.s.i. flow resistance may be provided in the fitting employed toconnect such discharge lines 149 to each bearing A, B, etc. lubricationopening (note FIG. 1). By this means, a

10 residual pressure to 700 p.s.i. is provided in the discharge linesand these low pressure cut-offs 66 are provided at each valve dischargeoutlet so that should the residual pressure in these lines fall belowthe nominal value of say 300 p.s.i., these valves will close off thedischarge passage, automatically producing a blockage.

Referring particularly to FIGS. 10 and 14, it will be noted that thefluid inlet to the valve lines up with the fluid outlet 98 and both arein line with the fluid passages 79 and 80 in the inlet and outlet endblocks in each manifold, respectively. Similarly, the lubricant passageis a throughbore lining up with the lubricant passages 70 and 81 in suchinlet and outlets blocks. This is also true of the high pressure by-passports 122. Each of the valves is also provided with aligned aperturesfor accommodation of the tie bolts 58, 59, 60 and 61 as are the inletand outlet end blocks provided with apertures 82.

Alternative System Referring now to FIG. 19, there is illustrated analternative lubricant system wherein a lubricant reservoir 15!) andelectrically driven pump 151 are provided in place of the lubricantsupply header as shown in FIG. 1. Electric motor 152 is employed todrive pump 151 to supply the requisite 2,000 p.s.i. pressure to thelubricant supply line 153 connecting the valve manifolds 5, 7 and 8 inseries in a manner identical to the connection of the lubricant supplyline 1 to such manifolds in FIG. 1. In such case, the motor driven pumpand control or starter takes the place of the solenoid operated shut-offvalve 4 in FIG. 1. With this arrangement, no accumulator is positionedbetween the lubricant and fluid supply lines. The solenoid valve 154 isemployed to open and close relief line 155, such relief line beingprovided with a 700 p.s.i. resistance check valve 156. Also, since thepump is electricially driven, a high-pressure relief line 157 isprovided with a check valve 158 providing high-pressure relief at, forexample, 4,000 p.s.i. leading back from the pump discharge to thereservoir. Thus with the shut ofi valve 154 open and the pump motor 152turned off, a residual line pressure in the line 153 of 700 p.s.i. willbe obtained. When the motor 152 is turned on the 4,000 p.s.i. reliefvalve 158 will lead back to the reservoir through line 157 should suchexcessive pressure be obtained. Control box 159 is provided controllingmotor 152 and solenoid valve 154 through line 160 and a bank of signallights and associated high-low pressure switches may be provided asshown at 37 in a manner identical to that shown in FIG. 1.

Pressure in the fluid supply line 162 may be provided through air drivenpump 163 supplied by air through line 164. Air pressure in line 164 iscontrolled by solenoid operated valve 165 supplying air from header 166.An air motor 167 is employed to control shut-off valve 168 in reliefline 169 with a 700 p.s.i. relief valve 170 also being provided. Suchair motor 167 will also be controlled by solenoid valve 165 controlledfrom the control box 169. As in the FIG. 1 embodiment, a pressure switch171 may be employed to indicate to the control center 159 the completionof the high pressure fluid cycle to stop operation of fluid pump 163 andopen relief line valve 168 permitting the excess of lubricant pressureover the fluid pressure to return the valves to their rest position.

Referring now to the electrical diagram in FIG. 20, the variouselectrical components illustrated may be employed to control the FIG. 1embodiment of the present system. Such components are wired betweensuitable mains and 181. In the control box 31, a timer motor 182 iscontrolled by a cut-out switch 183 and controls cycle switch 184 andsignal switch 185 with clutch solenoid 186 engaging and disengaging thetimer motor 182 which runs continuously. In operation, the timer willcontrol the cycle switch 185 to energize control relay 187 if the properreset contacts are closed as hereinafter described. Energization ofrelay 187 closes normally open contacts 188 to energize relay 189. Thisis a pilot circuit for starting both the lubricant and fluid systems.Energization of relay 189; closes both sets of contacts 190 and 191 withthe closing of contacts 190 energizing solenoid valve 12 (FIG. 1).Energization of this solenoid valve controls air motor 10 to openshut-01f valve 4 in the lubricant supply line 1. The closing of contacts191 energizes solenoid valve 18 starting the fluid pump 16 as well asoperating air motors 25 and 47 to close shut-ofi? valves 24 and 46respectively. With such solenoids energized, the system is now inoperation. 7

The high pressure switch 32 which is located in the fluid system lineafter the last manifold or in the last valve which is set forapproximately 3,000 p.s.i. indicates completion of the fluid cycle andenergizes reset relay 33 when such pressure is obtained at the end ofthe last manifold. Reset relay 33 closes normally open contacts 192 andopens normally closed contacts 193 deenergizing relay 187 opening bothcontacts 190 and 191 to deenergize solenoid valves 12 and 18 stoppingboth systems. Also the clutch will be engaged through solenoid 186 tostart the time interval until the next cycle.

High pressure switch 35 energizes signal lamp 36 in the signal lamp bank37 and low pressure or broken line switch 48, which is located in thefluid system aheadof the first manifold and set for-approximately 650p.s.i. indicating a broken line, may be employed in either system toenergize signal lamp 49. High pressure switch 38 is located betweenmanifold-s and 7 and is set for approximately 3,500 p.s.i., indicating amalfunction of the succeeding manifold, and such switch energizes signallamp 40; and finally high pressure switch 39 energizes signal lamp 41 inthe same manner as switches 35 and 38. It is noted that each of theswitches 32,35, 48 and 38 and 39 is'provided with a set of contacts inseries with control relay 194. Control relay 194 controls contacts 195in the timing cycle and Warning circuit in series with relay 187. Suchrelay 194 prevents the system starting and will cause an alarm if notreset at the proper time. Thus, all of the switches 32, '35, 48, .38 and39 must be properly set before the system can be placed in operation.The signal lamp 196 may be employed in series with control relay 187 toindicate when such relay is not energized through the cycle and signalswitches 1-84 and 185. respectively. It will, of course, beunderstoodthat the illustrated circuit is employed with only three manifolds ofvalves and accordingly only the appurtenant signaling switches areindicated. If an extensive system is employed, additional switches will,of' course, be employed.

it will now be seen that there has been provided not only a valvestructure but a centralized lubricating system capable of handlingeither grease or oil; of delivering such lubricant under pressure to allinterconnected bearings in measured but adjustable amounts; of signalingbearing discharge line leakageror stoppage through system pressurechange without interrupting operation of unaffected valves; and ofgiving visual indication of the precise point of operational failure.

Other modes of applying the principles of the invention may be employed,change being made as regards the details described, provided thefeatures stated in any of the following claims or the equivalent of suchbe employed.

I, therefore, particularly point out and distinctly claim as myinvention:

l. A centralized lubricating system comprising a lubricant supply lineand a fluid control line, a plurality of lubricant metering valvesserially interconnected in said lubricant supply line and said fluidline, means to place said lubricantsupply line at a substantiallyconstant line pressure; means to raise the pressure in said fluid lineabove the pressure in said lubricant line to cause discharge oflubricant through said lubricant metering valves, and means to lower thefluid pressure in said fluid line below thepressure in said lubricantsupply line again to cause discharge of lubricant through said lubricantvalves.

2. In a centralized lubricating system, a source of lubricant underpressure, a plurality of metering valves connected to said source oflubricant under pressure, a hydraulic fluid'circuit connected to saidmetering valves, said metering valves each having two lubricantdischarge outlets, and means to force lubricant through one saiddischarge outlet when the pressure of the hydraulic fluid exceeds thelubricant pressure, and means to force lubricant through the other saiddischarge outlet when such fluid pressure falls below such lubricantpressure. i

3. The system set forth in claim 2 including means to vary the fluidline pressure from substantially above such lubricant line pressure tosubstantially below such lubricant line pressure.

4. A centralized lubricating system comprising a lubricant supply line,means to pressurize said lubricant supply line, a plurality of meteringvalves connected in series in said lubricant supply line,two lubricantoutlets in each said metering valves, a fluid control line connectedparallel to said lubricant supply line and in series with said meteringvalves, said valves including means responsive to an excess of pressurein said fluid supply line over the pressure in said lubricant supplyline to force a metered quantity of lubricant through one said lubricantoutlet, and means responsive to an excess of pressurein said lubricantsupply line over the pressure in said fluid supply line to force ametered amount of lubricant through the other said lubricant outlet.

5. A centralized lubricating system as set forth in claim 4 includingmeans to create a pressure in said fluid control line substantially inexcess of the pressure in said lubricant supply line, and means torelieve the pressure in said fluid control line whereby the pressure insaid lubricant supply line will be substantially in excess of thepressure in said fluid control line.

6. A centralized lubricating system as set forth in claim 4 includingmeans to create a pressure in said fluid control line substantially inexcess of the pressure in said lubricant supply line, and meansresponsive to the attainment of such pressure in said fluid control linein the most remote portion of said system to relieve the pressure insaid fluid control line whereby the pressure in said lubricant supplyline will be substantially in excess of the pressure in said fluidcontrol line. 7

7. A centralized lubricating system comprising a lubricant supplysource, means to pressurize said lubricant supply, a plurality ofmetering valves connected to said including means responsive to anexcessive pressure of said fluid over lubricant pressure to force ametered quantity of lubricant through one of said lubricant outlets ineach said valve, and means responsive to an excessive pressure of saidlubricant over fluid pressure to force a metered amount of lubricantthrough the other said lubricant outlet in each said valve.

8. A centralized lubricating system as set forth in claim 7 wherein saidmetering valves each include apilot piston and a main piston, meansconnecting one end of said pilot piston to said fluid pressure source,and means connecting theother end of said pilot piston to said lubricantpressure source; and means responsive to movement of said pilot pistonto connect opposite ends of said main pistonwith said lubricant pressuresource.

9. A centralized lubricating system as set forth in claim 7 8 includingmeans responsive to reciprocation of said pilot 13 fold to the outletside of said manifold, said fluid by-pass line connecting the fluidinlet of said manifold to the fluid outlet of said manifold.

11. A centralized lubricating system as set forth in claim wherein saidby-pass line includes a pressure operated valve therein, and means toopen said valve upon the attainment of a predetermined high pressure insaid fluid supply.

12. A centralized lubricating system as set forth in claim 11 includinga passage around said high pressure by-pass valve, said passageincluding a relief valve adapted to permit relief of such fluid throughsuch by-pass passage.

13. A centralized lubricating system and the like comprising a meteringvalve having a main piston and a pilot piston, means connecting one endonly of said pilot piston to a source of lubricant under pressure, meansresponsive to movement of said pilot piston toward said one end toconnect said source of lubricant under presure to one end of said mainpiston, and means responsive to such movement of said pilot piston toport the opposite side of said main piston to a bearing and the like.

14. The system as set forth in claim 13 including fluid pressure meansto move said pilot piston.

15. A system as set forth in claim 14 wherein said pilot piston includesmeans alternately to connect opposite ends of said main piston with saidsource of lubricant under pressure upon movement of said pilot piston.

16. A system as set forth in claim 15 wherein said pilot piston includesmeans alternately to connect the opposite ends of said main piston toseparate bearing discharge lines upon reciprocation of said pilotpiston.

17. A system as set forth in claim 14 wherein said fluid pressure meansincludes alternate fluid passages for said pilot piston in the extremepositions thereof, said passages being open and closed by movement ofsaid main and pilot pistons.

18. A system as set forth in claim 17 wherein both said alternatepassages will be closed when said main and pilot pistons are in anout-of-phase position, and fluid pressure by-pass means operativeresponsive to such out-of-phase position of said main and pilot pistons.

19. A metering valve as set forth in claim 13 including a valve housingfor said metering valve, and fluid pressure passages therein adapted tooperate said pilot piston, said fluid passages therein being positionedsuch that said valve can be manifolded.

20. A centralized lubricating system comprising a source of lubricantunder pressure, a lubricant supply line leading therefrom; a pluralityof lubricant metering valves connected to said lubricant supply line; asource of fluid under pressure, a fluid supply line leading therefrom,means connecting said fluid supply line to said metering valves; andmeans simultaneously to pressurize said lubricant and fluid supply linesat high yet different pressures to operate said metering valves todispense lubricant therethrough, and means simultaneously to pressurizesaid lubricant and fluid supply lines with reversing differentialpressures and equalize the pressures in said fluid and lubricant supplylines after all such valves have been operated.

21. A centralized lubricating system as set forth in claim 20 whereineach said valve includes two lubricant outlets, lubricant beingdischarged through one said outlet when said supply lines arepressurized and through the other said outlet when said fluid supplyline is relieved.

22. A centralized lubricating system as set forth in claim 21 includingmanifolds of said valves, means adjacent each manifold adapted toindicate excessive pressure variance in said fluid supply line.

23. -A centralized lubricating system as set forth in 14 claim 22including means at the distal end of said system to relieve said systemin response to the obtaining of such high pressure in said fluid supplyline at such distal end.

24. A centralized lubricating system as set forth in claim 23 includingaccumulator means interconnecting said lubricant and fluid supply linesto equalize the atrest pressure in said system.

25. A centralized lubricating system as set forth in claim 20 includingpressure relief lines connected to said fluid and lubricant supplylines, shutoff valves in each said pressure relief line, and controlmeans to close said shutoff valves when said fluid and lubricant supplylines are pressurized at such high yet dilferent pressures.

26. A centralized lubricating system as set forth in claim 25 includingpump means operative thus to pressurize said lubricant and fluid supplylines, and means responsive to such pressure at the distal end of saidsystem to turn ofl said pump means and open said shutofi valves.

27. A centralized lubricating system as set forth in claim 20 includinga pressurized lubricant header, said lubricant supply line beingconnected thereto, a shutoff valve in said lubricant supply line, pumpmeans to pressurize said fluid supply line, and means simultaneously toopen said shutolf valve and energize said pump means thus to pressurizesaid lubricant and fluid supply lines.

28. A centralized lubricating system as set forth in claim 27 includingmeans simultaneously to relieve the pressure in said fluid supply lineand deenergize said pump means upon the attainment of a predeterminedhigh pressure at the distal end of such system.

29. A centralized lubricating system as set forth in claim 28 includingaccumulator means interconnecting said lubricant and fluid supply linesto equalize the at rest pressure in said system.

30. A system as set forth in claim 2 wherein said lubricant dischargeoutlets are each provided with a line connected to a bearing structureor the like, and means responsive to line failure resulting in anabnormal decrease in pressure in said line to block said line andprovide a visual signal at such line pin-pointing such line failure.

31. A centralized lubricating system comprising a lubricant supply lineand a fluid supply line, a plurality of lubricant metering valvesconnected to said lubricant and fluid supply lines each having alubricant discharge outlet; means simultaneously to pressurize saidlubricant and fluid supply lines at high yet different pressures tooperate said metering valves to dispense lubricant therethrough, saidlubricant discharge outlets each being provided with a line connectingsuch outlets to a bearing structure or the like, and means responsive tosaid latter line failure resulting in an abnormal decrease in pressurein said latter line to block said line and provide a visual signal atsuch line pin-pointing such line failure.

32. A centralized lubricating system as set forth in claim 9 whereineach said valve includes alternate fluid passages therethrough, movementof said pilot piston and the resulting movement of said main pistonclosing one of said alternate passages and opening the other to permitfluid flow therethrough similarly to operate the next succeeding valve.

References Cited in the file of this patent UNITED STATES PATENTS1,958,187 Dirkes May 8, 1934 2,038,287 Hawkes et al. Apr. 21, 19362,240,158 Hillis Apr. 29, 1941 2,719,603 Le Clair Oct. 4, 1955 2,973,058Bricout Feb. 28, 1961

